CN103423163A - Rotary compressor, and jet refrigeration circulating apparatus comprising it - Google Patents
Rotary compressor, and jet refrigeration circulating apparatus comprising it Download PDFInfo
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- CN103423163A CN103423163A CN2012101665906A CN201210166590A CN103423163A CN 103423163 A CN103423163 A CN 103423163A CN 2012101665906 A CN2012101665906 A CN 2012101665906A CN 201210166590 A CN201210166590 A CN 201210166590A CN 103423163 A CN103423163 A CN 103423163A
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Abstract
The invention relates to a rotary compressor, and a jet refrigeration circulating apparatus comprising it. The rotary compressor is characterized in that a motor and a compression mechanism having a refrigerant injection device are arranged in a sealed shell, the refrigerant injection device comprises a first injection hole arranged in a cylinder compression chamber and a second injection hole connected with a refrigerant injection loop arranged outside the shell, a valve operating cavity is arranged between the first injection hole and the second injection hole, an operating valve used for controlling the opening and closing of the first injection hole is arranged in the valve operating cavity, and an elastic component pressing the operating valve along a direction closing the second injection hole is arranged in the valve operating cavity. Valve holes are arranged on the outer rim of the operating valve, one end of a coil spring is crimped on the operating valve, the other end of the coil spring is crimped on a cylinder, and a refrigerant going through the second injection hole is injected into the first injection hole through the inside of the coil spring from the outside of the coil spring. The rotary compressor can prevent the compressor efficiency reduction caused by the injection of the refrigerant.
Description
Technical field
The present invention relates to a kind of rotary compressor, a kind of rotary compressor and comprise the injection freezing cycle device of this rotary compressor particularly, the injection rotary compressor that injects the cylinder compression chamber to liquid coolant by freeze cycle or gas coolant is relevant, can prevent from causing due to the refrigerant injection Efficiency Decreasing of compressor.
Background technique
The coolant injection system of rotary compressor is not singly prevent the torrid areas air-conditioning overheated, recent, and the overheated and raising heating capacity means that prevent that the predetermined refrigerant R32 adopted in the whole world is relevant are concerned.The coolant injection system has several schemes, and wherein, it is that the injection to refrigerant was optimized with the opportunity stopped according to the change of various operating conditions that one-way valve type sprays rotary compressor.But, one-way valve type spray injection apparatus in rotary compressor because the one-way valve perforate too early or the one-way valve closed pore too late, cause the refrigerant of each refrigerant infusion circuit to flow out to inlet hole, in addition, also, because the high pressure air of compressor is known from experience adverse current in the refrigerant infusion circuit, result can reduce refrigerating capacity and spray cooling effectiveness.
Patent documentation 1 Japanese documentation special permission is flat 5 (1993)-60085 rotary compressors openly
Summary of the invention
Purpose of the present invention aim to provide a kind of simple and reasonable, improve efficiency that one-way valve type sprays rotary compressor, prevent because refrigerant injects the Efficiency Decreasing that causes compressor, rotary compressor applied widely and comprises the injection freezing cycle device of this rotary compressor, to overcome deficiency of the prior art.
A kind of rotary compressor by this purpose design, be provided with motor and with the compressing mechanism of refrigerant injection device in seal casinghousing, its structure characteristic is the first hole hand-hole that the refrigerant injection device is included in perforate in the cylinder compression chamber, connected the second hand-hole at the refrigerant infusion circuit of the arranged outside of housing, be provided with the valve events chamber between the first hole hand-hole and the second hand-hole, be provided with the operating valve for control switch the second hand-hole in the valve events chamber, in the valve events chamber, be provided with along the elastic component of closing the second hand-hole direction push action valve.
Described elastic component is coil spring, be provided with valve opening on the outer rim of operating valve, one side pressure of coil spring is connected on operating valve, and the other end of coil spring is crimped on cylinder, and the refrigerant by the second hand-hole injects the first hole hand-hole from the outside of coil spring by the inboard of coil spring.
Described elastic component is coil spring, be provided with valve opening on the outer rim of operating valve, and valve opening is positioned at coil spring; One side pressure of coil spring is connected on operating valve, and the other end of coil spring is crimped on cylinder.
With respect to the internal diameter of the second hand-hole, the internal diameter of the first hole hand-hole is diminished.
With respect to the center of the second hand-hole, by the center-biased of the first hole hand-hole.
A kind of injection freezing cycle device that comprises rotary compressor, is characterized in that at least also comprising liquid coolant infusion circuit or the gas coolant infusion circuit of freeze cycle.
Coil spring in the present invention be due to by operating valve to the direction supercharging of closing valve seat, so compression chamber can postpone the perforate of the second hand-hole when low pressure is changed; In addition, before pressure and the refrigerant injection pressure of compression chamber reaches and equate, can close the second hand-hole; Therefore, can prevent that refrigerant from flowing out and to the adverse current of refrigerant infusion circuit to inlet hole.
The present invention can be applied to the improvement of the freezing cycle device of air conditioner, refrigerating machine, water heater etc., its have simple and reasonable, prevent because refrigerant injects the Efficiency Decreasing of compressor, the characteristics applied widely of causing.
The accompanying drawing explanation
Fig. 1 is in the embodiment of the present invention 1, carries the freeze cycle schematic diagram of the air conditioner of rotary compressor.
Fig. 2 is in embodiment 1, the longitudinal section schematic diagram of compressing mechanism.
Fig. 3 is in embodiment 1, the cross sectional representation of compressing mechanism during stroke A.
The master that Fig. 4 is the operating valve in embodiment 1 looks schematic diagram.
The master that Fig. 5 is the coil spring in embodiment 1 looks schematic diagram.
Fig. 6 is in embodiment 1, the cross sectional representation of compressing mechanism during stroke B.
Fig. 7 is in embodiment 1, the cross sectional representation of compressing mechanism during stroke C.
Fig. 8 is in embodiment 1, shows the schematic diagram on opportunity that refrigerant injects on the cylinder compression chamber.
Fig. 9 is in the embodiment of the present invention 2, the longitudinal section schematic diagram of refrigerant injection device.
Figure 10 is in the embodiment of the present invention 3, the cross sectional representation of refrigerant injection device.
Figure 11 is in the embodiment of the present invention 4, carries the freeze cycle schematic diagram of the air conditioner of rotary compressor.
In figure: R is compressor, P is compressing mechanism, M is motor, E is the refrigerant injection device, 2 is housing, 3 is outlet pipe, 4 is four-way valve, 5 is indoor heat converter, 6 is outdoor heat converter, 7 is Twoway valves, 8 is expansion valve, 13 is liquid-storage container, 14 is suction pipe, 15 is capillary tube, 16 is the refrigerant infusion circuit, 17 is coolant injection tube, 22 is inlet hole, 23 is cylinder, 24 is compression chamber, 25 is main bearing, 26 is supplementary bearing, 27 is eccentric crankshaft, 28 is piston, 29 is slide plate, 32 is the cylinder cross-drilled hole, 33 is conduit, 34 is valve seat, 35 is coil spring, 36 is operating valve, 37 is valve opening, 39 is the valve events chamber, 40 is the first hand-hole, 45 is the second hand-hole, 50 is gas-liquid separator, 51 is liquid coolant.
Embodiment
Below in conjunction with drawings and Examples, the invention will be further described.
Embodiment 1
Referring to Fig. 1, mean that carrying liquid sprays the refrigeration of the air conditioner of rotary compressor R, the freeze cycle of heating dual-purpose.Between indoor heat converter 5 and outdoor heat converter 6, be provided with expansion valve 8 with and the one-way valve of front and back, connect an end of refrigerant infusion circuit 16 between these two one-way valves.The other end of this refrigerant infusion circuit 16 is connected with the coolant injection tube 17 in being arranged on rotary compressor R.In addition, Twoway valves 7 and capillary tube 15 are set in refrigerant infusion circuit 16.Therefore, no matter be refrigeration or heating mode, the liquid coolant of freeze cycle also can flow into coolant injection tube 17.
Referring to Fig. 2, expression is the longitudinal section schematic diagram of the detail display of compressing mechanism P and refrigerant injection device E, and Fig. 3 is the cross sectional representation of compressing mechanism.
Be provided with motor M and with the compressing mechanism P of refrigerant injection device E in seal casinghousing 2, refrigerant injection device E be included in perforate in cylinder compression chamber 24 the first hole hand-hole 40, connected the second hand-hole 45 at the refrigerant infusion circuit 16 of the arranged outside of housing 2, between the first hole hand-hole 40 and the second hand-hole 45, be provided with valve events chamber 39, be provided with for the operating valve 36 of control switch the second hand-hole 45 in valve events chamber 39, be provided with in valve events chamber 39 along the elastic component of closing the second hand-hole 45 direction push action valves 36.
On the front end of the cylinder cross-drilled hole 32 of cylinder 23, first hand-hole 40 perforate on compression chamber 24.The first hand-hole 40, for the circumferential distance of the inlet hole 22 that at utmost extends to the compression chamber perforate, relatively approaches slide plate 29.
Be pressed at cylinder cross-drilled hole 32 on the front end of conduit 33 and be provided with the second hand-hole 45, be equipped with valve seat 34 on the perforate end of the second hand-hole 45.The coil spring 35 that is provided with operating valve 36 and operating valve 36 is compressed towards valve seat 34 in the valve events chamber 39 by forming between the first hand-hole 40 and the second hand-hole 45.
Connected coolant injection tube 17 on the perforate end of conduit 33.By above structure, complete refrigerant injection device E.And the external diameter of refrigerant injection device E and valve events chamber 39 are due to the needs of explanation, the ratio actual design of description is larger.
Elastic component is coil spring 35, is provided with valve opening 37 on the outer rim of operating valve 36, and a side pressure of coil spring 35 is connected on operating valve 36, and the other end of coil spring 35 is crimped on cylinder.
Referring to Fig. 3-Fig. 5, operating valve 36 is the tabular circular valves with six valve openings 37, and the central part of operating valve 36 is arranged on valve seat 34 for controlling the switch of the second hand-hole 45.The central part of operating valve 36 does not arrange valve opening, therefore can be for the second hand-hole 45 on seal valve seat 34.Valve opening 37 is that the refrigerant flowed out from the second hand-hole 45 is discharged to the stream the first hand-hole 40, the function of valve opening 37 restricted cold medium fluxes.
Two ends are polished the coil spring 35 after processing, when the cold medium flux from the second hand-hole 45 to action chamber 39 is many, as shown in Figures 2 and 3, can be packed together to the snubber of operating valve 36.Therefore, the gap between valve seat 34 and operating valve 36 becomes maximum, maintains the gap of refrigerant passage.On the contrary, when from the second hand-hole 45, cold medium flux out reduces, the coil spring 35 of compression starts elongation, and operating valve 36 is fixing in valve seat 34.
Therefore, the present invention is not singly the design (aspect such as internal diameter) of the second hand-hole 45 and the first hand-hole 40, due to the design of coil spring 35, can realize opportunity of switch of the second hand-hole 45 and the optimization of coolant quantity.At this, the valve opening 37 of the operating valve 36 in embodiment 1 is at coil spring 35 open interiors.And, as can resiliency urged operating valve 36 just passable as coil spring 35, can be not limited to design disclosed herein, can realize design.
Next, according to disclosed technological scheme of the embodiment 1, illustrate: the action relationships of the rotation of piston 28 and operating valve 36 and the effect of coil spring 35.
When stroke A, as shown in Figure 3, the angle of rotation from slide plate 29De center to piston 28 means with θ.From θ=0 a ° angle of rotation, advance, for example, by inlet hole 22 (, θ=25 °) afterwards, the refrigerant injection pressure Pi of the second hand-hole 45 is higher than the pressure P m of compression chamber 24, i.e. Pi>Pm.Therefore, operating valve 36 fixing in valve seat 34 breaks away from and floats from valve seat 34, and the order that refrigerant is pressed operating valve 36, the first hand-hole 40, compression chamber 24 from the second hand-hole 45 is injected, and reduces the delivery temperature of compression chamber.Because this refrigerant injects effect, can reduce compression chamber 24 effluent air temp, motor M and oil temperature are controlled in allowed band.
When stroke B, as shown in Figure 6, the piston rotation angle θ continues forward, and the gas in compression becomes high pressure, and before Pi=Pm, due to the rebounding force of the coil spring 35 compressed, operating valve 36 is fixing on valve seat 34, and the refrigerant that stops compressor chamber 24 injects.Therefore, can prevent the effect due to coil spring 35, pressurized gas, from compression chamber 24 adverse currents to coolant injection tube 17, cause closing of operating valve 36 slower.That is,, before Pi<Pm, the second hand-hole 45 is to be in closed pore state.
When stroke C, as shown in Figure 7, the piston rotation angle θ continues forward, the periphery of piston 28 by the first hand-hole 40 (for example, θ=330 °) moment, because the first hand-hole 40 is the low pressure sides (now, the pressure P s of low pressure side) that connect compression chamber 24, pressure difference Δ p be in maximum rating (due to Pi now>>Ps).But, due to the effect of coil spring 35, operating valve 36 can't spin off at once from valve seat 34, from the second hand-hole 45 to first hand-holes 40, the refrigerant that even flows to compression chamber 24, flow slack-off.That is, the periphery of piston 28 is by after inlet hole 22, gets started the 24 injection refrigerants from the first hand-hole 40 to compression chamber.Therefore, because 22 refrigerant has leakage from coolant injection tube 17 to inlet hole, can prevent in advance the refrigerating capacity loss.
In order to be had, be equipped with and comparison when being equipped with above-mentioned coil spring 35, Fig. 8 means that the pressure of piston rotation angle θ and compression chamber 24 changes and the relation of refrigerant injection.Transverse axis means the piston rotation angle θ, and the longitudinal axis means pressure P (θ), and wherein, Ps is suction pressure, and Pi is jet pressure, and Pd is head pressure.Curve C is the pressure history of compression chamber 24.N means the state of nothing outfit coil spring 35 in valve events chamber 39, and Y means the scope from start to stop that the refrigerant under the state that is equipped with coil spring 35 injects.
Without under the state that is equipped with coil spring (N), the piston rotation angle θ is to start the filling liquid refrigerant in 330 °, stops injecting on when θ=195 °.
Be equipped with under the state of coil spring (Y), the piston rotation angle θ starts to inject refrigerant after surpassing 0 °, on about θ=1180 °, stops injecting.That is, due to the effect of coil spring 35, can postpone the perforate of the second hand-hole 45, in addition, also mean to shift to an earlier date closed pore.
Above-mentioned result is illustrated in without under the state that is equipped with coil spring (N), due to too early filling liquid refrigerant, can cause the cylinder inlet hole to leak, and due to the late release of one-way valve, can cause the refrigerant infusion circuit generation adverse current from compression chamber.But, be equipped with under the state of coil spring (Y), filling liquid refrigerant too early not, in addition, due to closed check valve morning, so adverse current can not occur.
If think further to bring into play the effect of coil spring 35, can further increase the elastic force of coil spring 35.At this moment, the elapsed time of injecting due to liquid coolant can postpone to inject stop time and can shift to an earlier date, so inject beginning and the scope that stops can be dwindled.But, as described in Example 1, there is the one-way valve type spray regime of operating valve 36, can easily increase and decrease the resistance of the first hand-hole 40, the second hand-hole 45 and operating valve 36 on principle.Therefore, can inject a large amount of refrigerants to compression chamber in short time or small angle range.
Next, in the running of the rotary compressor with injection apparatus in the past, owing to closing Twoway valves, can block the refrigerant infusion circuit, the pressure of refrigerant injection device can be compressed the impact of cavity pressure.While being each piston rotation, the high temperature and high pressure gas of compression chamber can flow to refrigerant injection device and refrigerant infusion circuit, in addition, because they flow out from compression chamber, that is to say due to respiratory movement, and expansion losses again can occur.
But embodiment 1, due to the pressurized effect of coil spring 35, can prevent respiratory movement.That is,, in embodiment 1, the pressure oscillation of the compression chamber produced in the running about compressor, do not produce in the action situation at operating valve 36, can remain fixed in the action on valve seat 34.Therefore, above-mentioned expansion losses again is difficult to produce, so be favourable to the minimizing of refrigerating capacity loss.
As above-mentioned, the present invention is owing in the refrigerant injection device having the such operating valve of one-way valve, having appended coil spring, could realize easily the improved efficiency of injection rotary compressor.In addition, due to the elastic force of having adjusted coil spring, easy implementation efficiency optimization.
In embodiment 1, close Twoway valves and while stopping spraying, the second hand-hole 45 is because operating valve 36 can continue to keep closed pore state in compressor operation.But the high pressure air of compression chamber 24 is known from experience inflow valve events chamber 39.These pressurized gas and compression chamber 24 exchange outflow in low pressure Ps, and refrigerating capacity is reduced, and become clearance volume, so become the reason of expansion losses again.
Solve this problem, please see embodiment 2, as shown in Figure 9: with respect to the internal diameter of the second hand-hole 45, the internal diameter of the first hand-hole 40 is diminished.The refrigerant of discharging from the valve opening 37 of operating valve 36 in addition, flows into the first hand-hole 40 from the outside of coil spring 35 by its inside.
Consequently: due to the internal diameter that can dwindle valve events chamber 39, so can dwindle clearance volume.And, with respect to embodiment 1, dwindled the internal diameter of operating valve 36, can further dwindle the internal diameter in valve events chamber 39.As above-mentioned said, the design of valve events chamber and coil spring is according to purport of the present invention, can realize variation.
All the other are not stated part and see embodiment 1, repeat no more.
When the position of opening of the first hand-hole 40 with respect to compression chamber 24, the closer to slide plate 29 here, the expansion losses again caused due to clearance volume can reduce, and also can enlarge the circumferential distance between the first hand-hole 40 and inlet hole 22.According to this purport, as shown in figure 10: relative the second hand-hole 45, during biasing, the first hand-hole 40 approaches slide plate 29.
All the other are not stated part and see embodiment 2, repeat no more.
Shown in embodiment 1: disclosed liquid coolant injection rotary compressor is in the situation that, without basic change, use the gas coolant injection rotary compressor.For example, in embodiment 1, can, by adjusting the gas channel of disclosed operating valve and hand-hole, as the gas coolant injection rotary compressor, adopt.
All the other are not stated part and see embodiment 3, repeat no more.
Finally, from embodiments of the invention 1 to embodiment 4, above-mentioned disclosed technological scheme can be applied in the injection rotary compressor be comprised of 2 cylinders or in 2 stage compression type rotary compressors.In addition, above-mentioned disclosed technological scheme is not limited only to air conditioner, and refrigerating machine, water heater etc. also can adopt.
Claims (6)
1. a rotary compressor, be provided with motor (M) and with the compressing mechanism (P) of refrigerant injection device (E) in seal casinghousing (2), it is characterized in that refrigerant injection device (E) is included in the first hole hand-hole (40) of perforate in cylinder compression chamber (24), connected the second hand-hole (45) at the refrigerant infusion circuit (16) of the arranged outside of housing (2), be provided with valve events chamber (39) between the first hole hand-hole (40) and the second hand-hole (45), be provided with the operating valve (36) for control switch the second hand-hole (45) in valve events chamber (39), in valve events chamber (39), be provided with along the elastic component of closing the second hand-hole (45) direction push action valve (36).
2. rotary compressor according to claim 1, is characterized in that described elastic component is coil spring (35), be provided with valve opening (37) on the outer rim of operating valve (36), and valve opening (37) is positioned at coil spring (35); It is upper that one side pressure of coil spring (35) is connected on operating valve (36), and the other end of coil spring (35) is crimped on cylinder.
3. rotary compressor according to claim 1, it is characterized in that described elastic component is coil spring (35), be provided with valve opening (37) on the outer rim of operating valve (36), one side pressure of coil spring (35) is connected on operating valve (36), the other end of coil spring (35) is crimped on cylinder, and the refrigerant by the second hand-hole (45) injects the first hole hand-hole (40) from the outside of coil spring (35) by the inboard of coil spring (35).
4. rotary compressor according to claim 1, is characterized in that the internal diameter with respect to the second hand-hole (45), and the internal diameter of the first hole hand-hole (40) is diminished.
5. according to the arbitrary described rotary compressor of claim 1 to 4, it is characterized in that the center with respect to the second hand-hole (45), by the center-biased of the first hole hand-hole (40).
6. an injection freezing cycle device that comprises the described rotary compressor of claim 1, is characterized in that at least also comprising liquid coolant infusion circuit or the gas coolant infusion circuit of freeze cycle.
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| CN201210166590.6A CN103423163B (en) | 2012-05-24 | 2012-05-24 | Rotary compressor and the injection freezing cycle device including the rotary compressor |
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| CN201210166590.6A CN103423163B (en) | 2012-05-24 | 2012-05-24 | Rotary compressor and the injection freezing cycle device including the rotary compressor |
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Cited By (10)
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| CN103727039A (en) * | 2014-01-08 | 2014-04-16 | 广东美芝制冷设备有限公司 | Two-stage compression rotary compressor, pump body assembly of two-stage compression rotary compressor, and air conditioning system |
| CN104806522A (en) * | 2015-05-13 | 2015-07-29 | 广东美芝制冷设备有限公司 | Rotating compressor and refrigeration device with same |
| JP6197922B1 (en) * | 2016-06-22 | 2017-09-20 | ダイキン工業株式会社 | Compressor and valve assembly |
| JP2017190698A (en) * | 2016-04-12 | 2017-10-19 | 株式会社富士通ゼネラル | Rotary Compressor |
| CN107476973A (en) * | 2016-04-12 | 2017-12-15 | 富士通将军股份有限公司 | Rotary compressor |
| JP2018076796A (en) * | 2016-11-08 | 2018-05-17 | 株式会社富士通ゼネラル | Rotary Compressor |
| CN109891095A (en) * | 2016-11-02 | 2019-06-14 | 大金工业株式会社 | Compressor |
| CN110469510A (en) * | 2018-05-11 | 2019-11-19 | 上海海立电器有限公司 | Compressor |
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| CN114286893A (en) * | 2019-08-30 | 2022-04-05 | 大金工业株式会社 | Rotary compressor |
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| CN109312747A (en) * | 2016-06-22 | 2019-02-05 | 大金工业株式会社 | Compressor and valve assembly |
| CN109891095A (en) * | 2016-11-02 | 2019-06-14 | 大金工业株式会社 | Compressor |
| JP2018076796A (en) * | 2016-11-08 | 2018-05-17 | 株式会社富士通ゼネラル | Rotary Compressor |
| CN110469510B (en) * | 2018-05-11 | 2021-11-09 | 上海海立电器有限公司 | Compressor |
| CN110469510A (en) * | 2018-05-11 | 2019-11-19 | 上海海立电器有限公司 | Compressor |
| CN111749901A (en) * | 2019-03-29 | 2020-10-09 | 上海海立电器有限公司 | Check valve and rotor compressor |
| CN114286893A (en) * | 2019-08-30 | 2022-04-05 | 大金工业株式会社 | Rotary compressor |
| CN114286893B (en) * | 2019-08-30 | 2023-08-25 | 大金工业株式会社 | rotary compressor |
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